SE450944B - RANGEVEXELLADA FOR MOTOR VEHICLES - Google Patents
RANGEVEXELLADA FOR MOTOR VEHICLESInfo
- Publication number
- SE450944B SE450944B SE8306735A SE8306735A SE450944B SE 450944 B SE450944 B SE 450944B SE 8306735 A SE8306735 A SE 8306735A SE 8306735 A SE8306735 A SE 8306735A SE 450944 B SE450944 B SE 450944B
- Authority
- SE
- Sweden
- Prior art keywords
- ring
- coupling
- sleeve
- gear
- synchronizing
- Prior art date
Links
Classifications
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
- B60K17/00—Arrangement or mounting of transmissions in vehicles
- B60K17/04—Arrangement or mounting of transmissions in vehicles characterised by arrangement, location, or kind of gearing
- B60K17/043—Transmission unit disposed in on near the vehicle wheel, or between the differential gear unit and the wheel
- B60K17/046—Transmission unit disposed in on near the vehicle wheel, or between the differential gear unit and the wheel with planetary gearing having orbital motion
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
- F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
- F16H3/46—Gearings having only two central gears, connected by orbital gears
- F16H3/48—Gearings having only two central gears, connected by orbital gears with single orbital gears or pairs of rigidly-connected orbital gears
- F16H3/52—Gearings having only two central gears, connected by orbital gears with single orbital gears or pairs of rigidly-connected orbital gears comprising orbital spur gears
- F16H3/54—Gearings having only two central gears, connected by orbital gears with single orbital gears or pairs of rigidly-connected orbital gears comprising orbital spur gears one of the central gears being internally toothed and the other externally toothed
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
- F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
- F16H3/78—Special adaptation of synchronisation mechanisms to these gearings
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H37/00—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00
- F16H37/02—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings
- F16H37/04—Combinations of toothed gearings only
- F16H37/042—Combinations of toothed gearings only change gear transmissions in group arrangement
- F16H37/046—Combinations of toothed gearings only change gear transmissions in group arrangement with an additional planetary gear train, e.g. creep gear, overdrive
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Transportation (AREA)
- Structure Of Transmissions (AREA)
- Mechanical Operated Clutches (AREA)
- General Details Of Gearings (AREA)
- Arrangement Of Transmissions (AREA)
- Arrangement And Driving Of Transmission Devices (AREA)
Description
15 20 25 30 35 450 944 hâllaren och ringhjulet vid körning på den högre växeln. Det upptvinnade momentet leds via planethjulshållaren. utgående axeln. kopplíngsringen. kopplíngshylsan och ringhjulshållaren tillbaka till ringhjulet och beror till storleken på förhållan- det i radie mellan solhjulet och ringhjulet. Genom att så många komponenter måste dímensioneras för höga belastningar blir rangeväxeln relativt dyr. Den blir dessutom utrymmeskrävande i axiell led. 15 20 25 30 35 450 944 the holder and the ring gear when driving in the higher gear. The recovered torque is led via the planetary gear holder. output shaft. clutch rings. the clutch sleeve and ring gear holder back to the ring wheel and depends on the size of the ratio in the radius between the sun gear and the ring wheel. Because so many components have to be dimensioned for high loads, the range gear becomes relatively expensive. It also becomes space-consuming in the axial joint.
Vid en annan känd rangeväxellåda utnyttjas själva ringhjulet som kopplingshylsa. varvid ringhjulet är axiellt förskjutbart till-ingrepp med kopplingsringar framför resp. bakom planet- växeln. Denna konstruktion eliminerar visserligen några av kom- ponenterna hos den ovan beskrivna växellådan. men i gengäld skapas flera nackdelar. För det första måste planetväxeln pla- ceras längre bak än vid det ovan beskrivna utförandet för att ge plats för kopplingsring med synkronisering framför planet- växeln. vilket betyder att "överhänget" blir större. dvs. läng- den av huvudaxeln (ingående axeln) mellan lagringen på ingångs- sidan och den inre axeländen med solhjulet. Eftersom planet- växeln tjänstgör som inre lagring för den utgående axeln, är det emellertid angeläget att hålla överhänget så litet som möjligt. Detta på grund av att utböjningar av huvudaxeln medför förflyttningar av planetväxeln ur det ideala läget. Dessa för- flyttningar blir större ju större överhänget är och medför snedställning av kugghjulen med ogynnsamt kuggingrepp som följd. För det andra måste kopplíngsringar och synkroniserings- anordningar anpassas till ringhjulets diameter. vilket betyder att de exempelvis får så stor diameter, att det inte är möjligt att utnyttja samma komponenter som i basväxellådan.In another known range gearbox, the ring gear itself is used as a coupling sleeve. wherein the ring wheel is axially displaceable engagement with coupling rings in front of resp. behind the planetary gear. Admittedly, this construction eliminates some of the components of the gearbox described above. but in return several disadvantages are created. First, the planetary gear must be placed further back than in the embodiment described above to make room for a clutch ring with synchronization in front of the planetary gear. which means that the "overhang" becomes larger. i.e. the length of the main shaft (input shaft) between the bearing on the input side and the inner shaft end with the sun gear. However, since the planetary gear unit serves as internal storage for the output shaft, it is important to keep the overhang as small as possible. This is because deflections of the main axis cause displacements of the planetary gear out of the ideal position. These displacements become larger the larger the overhang and causes the gears to skew with unfavorable gear engagement as a result. Second, clutch rings and synchronizing devices must be adapted to the diameter of the ring gear. which means, for example, that they have such a large diameter that it is not possible to use the same components as in the base gearbox.
Syftet med föreliggande uppfinning är att åstadkomma en range- växellåda av i inledningen angivet slag. vilken kan byggas upp av färre komponenter. i synnerhet komponenter utsatta för upp- tvinnat moment. än den förstnämnda kända rangeväxeln. under bi- behållande av minimalt överhäng och med möjlighet att utnyttja standardkomponenter för synkroniseringarna. .#7 10 15 20 25 30 35 450 944 Detta uppnås enligt uppfinningen genom att ringhjulet är ovrid- bart förbundet med en koncentriskt med den utgående axeln an- ordnad, som ringhjulsbärare tjänstgörande kopplingshylsa. vil-I ken är axiellt förskjutbar mellan ett första kopplingsläge.-i vilket den upprättar ovridbar förbindelse mellan ringhjulet och den utgående axeln. och ett andra kopplingsläge. i vilket den upprättar ovridbar förbindelse mellan rínghjulet och huset.The object of the present invention is to provide a range gearbox of the type indicated in the introduction. which can be built up of fewer components. in particular components exposed to twisted torque. than the former known range gear. while maintaining a minimal overhang and with the possibility of using standard components for the synchronizations. # 7 10 15 20 25 30 35 450 944 This is achieved according to the invention in that the ring wheel is inextricably connected to a coupling sleeve serving concentrically with the output shaft arranged as a ring wheel carrier. which is axially displaceable between a first clutch position, in which it establishes a non-rotatable connection between the ring gear and the output shaft. and a second switching position. in which it establishes an irreversible connection between the ring wheel and the housing.
Vid utförandet enligt uppfinningen kan kopplingsringen för högrange vara fast förbundenmed planethjulshâllarens nav.» vilket innebär att det upptvinnade momentet leds från planet- hjulshâllaren till ringhjulet enbart via kopplingsringen och kopplingshylsan. Kopplingsríngen för lâgrange kan vara fast förbunden med husets bakre gavel. vilket eliminerar behovet av den tidigare nämnda mellanväggen. Detta tillsammans med bort- fallet av dels en på den utgående axeln roterbart lagrad ring- hjulsbärare och dels en med den utgående axeln fast förbunden kopplingsring ger en i axelriktningen optimalt kort växellåda.In the embodiment according to the invention, the coupling ring for high-range can be fixedly connected to the hub of the planetary gear holder. " which means that the recovered torque is led from the planetary gear holder to the ring gear only via the coupling ring and the coupling sleeve. The coupling ring for bearing range can be fixedly connected to the rear end of the house. which eliminates the need for the previously mentioned partition. This, together with the absence of a ring gear carrier rotatably mounted on the output shaft and a coupling ring fixedly connected to the output shaft, gives an optimally short gearbox in the axial direction.
Utförandet gör det möjligt att dimensionera kopplingshylsan med mindre diameter än rínghjulet, vilket direkt har till följd att växlingsgaffel. synkroniseringskonor och kopplingsríngar blir mindre och billigare än vid det kända utförandet. Qär själva ringhjulet utnyttjas som kopplíngshylsa.The design makes it possible to dimension the coupling sleeve with a smaller diameter than the ring wheel, which directly results in a shift fork. synchronizing cones and coupling rings become smaller and cheaper than in the known embodiment. The ring gear itself is used as a coupling sleeve.
Uppfinningen beskrives närmare under hänvisning till på bifo- gade-ritníng visade utföringsexempel. där figuren visar ett längdsnitt genom den övre halvan av en till en basväxellåda ansluten rangeväxellåda.The invention is described in more detail with reference to exemplary embodiments shown in the accompanying drawing. where the figure shows a longitudinal section through the upper half of a range gearbox connected to a base gearbox.
I figuren betecknar 1 den bakre delen av huset till en bas- växellåda, vid vilken en fläns 2 på ett framåt öppet hus 3 till en rangeväxellåda är fastbultad. Husets l bakre gavel 4 bildar således samtidigt rangeväxelhusets 3 främre gavel. Baslådan har en utgående axel 5. som är lagrad i ett lager 6 och inskjuter i rangeväxellâdans hus 3. Axeln 5 bildar rangeväxellädans ingå- ende axel, som via en generellt med 7 betecknad planetväxel är kopplad till en utgående axel 8 försedd med en fläns för an- slutning till fordonets kardanaxel. ..,..._._..._..._.___-__._..___...___-.... l ._ ___. _ 10 15 20 25 30 35 450 944 Planetväxeln 7 innefattar ett med den ingående axeln 5 fast förbundet solhjul 9. vilket ingríper med planethjul 10. som är lagrade på axlar ll uppburna av en planethjulshållare 12. vil- ken i sin tur via ett splinesförband 13 är ovridbart fäst på den utgående axeln 8. Planethjulen 10 ingríper med ett ringhjul 14. som uppvisar invändiga splines 15 i ingrepp med utvändiga splines 16 på en ringformig fläns 17. vilken är utformad i ett I stycke_med en kopplingshylsa 18. En lâsring 19 i ett spår i ringhjulet fixerar delarna axiellt. Hylsan 18 är axiellt för- skjutbar med hjälp av en icke visad. till fordonets växelmeka- nism kopplad skiftgaffel.In the figure, 1 denotes the rear part of the housing of a base gearbox, in which a flange 2 of a forwardly open housing 3 of a range gearbox is bolted. The rear end 4 of the housing 1 thus simultaneously forms the front end of the range gear housing 3. The base box has an output shaft 5. which is mounted in a bearing 6 and projects into the housing of the range gearbox 3. The shaft 5 forms the input shaft of the range gear, which is connected via a planetary gear generally designated 7 to an output shaft 8 provided with a flange for connection to the PTO shaft of the vehicle. .., ..._._..._..._.___-__._..___...___-.... l ._ ___. The planetary gear 7 comprises a sun gear 9 fixedly connected to the input shaft 5, which engages with planet wheels 10 which are mounted on shafts 11 supported by a planet gear holder 12. which in turn via a spline joint 13 is non-rotatably attached to the output shaft 8. The planet gears 10 engage a ring gear 14. having internal splines 15 engaged with outer splines 16 on an annular flange 17. which is formed integrally with a coupling sleeve 18. A locking ring 19 in a groove in the ring gear fixes the parts axially. The sleeve 18 is axially displaceable by means of one not shown. shift fork connected to the vehicle's gear mechanism.
Kopplingshylsan 18 har invändiga tänder 20. som i det i figuren visade läget ingríper med motsvarande tänder på en kopplings- ring 21. som via ett splinesförband 22 är ovridbart förbunden med planethjulshållarens 12 nav. Kopplingsringen 2l är utformad med en synkroniseringskona 23. vilken uppbär en synkronise- ringsring 24 i ingrepp med kopplingshylsans 18 tänder 20. En motsvarande tandad kopplingsring 25 med synkroniseringskona 26 uppbärande en synkroniseringsríng 27 är fixerad mot rangeväxel- husets 3 bakre gavel av en ringformig platta 28. som med utvän- diga tänder 29 ingríper med på husets 3 insida utformade tänder 30 och med invändiga tänder 31 ingríper med kopplingsringens 25 tänder. I Kopplingshylsans 18 tänder 20 uppvisar fördjupningar 32 och 33. avsedda att upptaga en mellan synkroniseringsringarna 24 och 27 anordnad ringformig fjäder 34. som har till uppgift att över- föra anpressningskraften från hylsan 18 till synkroniserings- ringarna vid växling. Fördjupningarna 32 och 33 bildar således i princip ett par ringformiga spår mellan vilka fjädern 34 för- flyttas vid växling. varvid fjädern under växlingsrörelsen komprimeras av den mellan fördjupningarna eller spåren bildade àsen 35.The coupling sleeve 18 has internal teeth 20. which in the position shown in the figure engage with corresponding teeth on a coupling ring 21. which is inextricably connected via a spline connection 22 to the hub of the planetary gear holder 12. The coupling ring 211 is formed with a synchronizing cone 23. which carries a synchronizing ring 24 in engagement with the teeth 20 of the coupling sleeve 18. A corresponding toothed coupling ring 25 with synchronizing cone 26 supporting a synchronizing ring 27 is fixed to the rear end of the range gear housing 3 by an annular plate 28 which engages with external teeth 29 with teeth 30 formed on the inside of the housing 3 and with internal teeth 31 engages with the teeth of the coupling ring 25. In the teeth 20 of the coupling sleeve 18, they have depressions 32 and 33 intended to receive an annular spring 34 arranged between the synchronizing rings 24 and 27, which has the task of transmitting the pressing force from the sleeve 18 to the synchronizing rings when changing. The depressions 32 and 33 thus in principle form a pair of annular grooves between which the spring 34 is moved when changing. wherein the spring during the shifting movement is compressed by the axis 35 formed between the depressions or grooves.
I det i figuren visade läget hos kopplingshylsan 18 är ringhju- let 14 låst mot rotation relativt planethjulsbäraren 12 genom 10 15 450 944 att kopplíngshylsans tänder ingríper med kopplíngsríngens 21 tänder. Planetväxeln är sålunda låst. varvid dírektdrívníng er- hålles mellan den in- och utgående axeln. Vid förskjutning av kopplíngshylsan 18 och med denna även rínghjulet 14 åt höger í figuren fríkopplas först hylsan 18 från kopplíngsríngens tän- der. Efter en víss förskjutningssträcka träffar ringfjädern 34 den motstående synkroníseríngsríngen 27 och pressar denna mot hopplíngsríngens 25 kona 26. varvid uppbromsníngen av kopp- língshylsan och rínghjulet inleds. Under den fortsatta för- skjutníngen av hylsan 18 komprímeras fjädern 34 genom samverkan mellan de sneda kantytorna på spåret 33 och fjädern 34 och för- skjuts till slut över åsen 35 till spåret 32. I detta läge är synkroníseríngsarbetet fullbordat och kopplingshylsan kan bríngas i ingrepp med kopplíngsríngen 25 för att låsa rínghju- let 14-mot huset.In the position of the coupling sleeve 18 shown in the figure, the ring wheel 14 is locked against rotation relative to the planet gear carrier 12 by 450 944 that the teeth of the coupling sleeve engage with the teeth of the coupling ring 21. The planetary gear is thus locked. whereby direct drive is obtained between the input and output shafts. When the coupling sleeve 18 is displaced and with it also the ring wheel 14 to the right in the figure, the sleeve 18 is first disengaged from the teeth of the coupling ring. After a certain displacement distance, the ring spring 34 strikes the opposite synchronizing ring 27 and presses it against the cone 26 of the hopping ring 25, whereby the braking of the coupling sleeve and the ring wheel begins. During the continued displacement of the sleeve 18, the spring 34 is compressed by co-operation between the oblique edge surfaces of the groove 33 and the spring 34 and is finally displaced over the ridge 35 to the groove 32. In this position the synchronizing work is completed and the coupling sleeve can be brought into engagement with the coupling ring 25 for locking the ring wheel 14 against the housing.
Claims (5)
Priority Applications (8)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
SE8306735A SE450944B (en) | 1983-12-06 | 1983-12-06 | RANGEVEXELLADA FOR MOTOR VEHICLES |
GB08429995A GB2151316B (en) | 1983-12-06 | 1984-11-28 | Range gearbox for motor vehicles |
US06/676,411 US4667538A (en) | 1983-12-06 | 1984-11-28 | Range gearbox for motor vehicles having an axially shiftable ring gear |
IT49256/84A IT1178350B (en) | 1983-12-06 | 1984-12-05 | IMPROVEMENT IN ADDITIONAL SPEED CHANGES FOR VEHICLES |
FR848418562A FR2556067B1 (en) | 1983-12-06 | 1984-12-05 | DEMULTIPLICATION BOX FOR MOTOR VEHICLES |
JP59258400A JPH0788860B2 (en) | 1983-12-06 | 1984-12-06 | Range gear box for automobile |
DE3444562A DE3444562C2 (en) | 1983-12-06 | 1984-12-06 | Manual transmission for motor vehicles |
US07/445,051 USRE33428E (en) | 1983-12-06 | 1989-11-24 | Range gearbox for motor vehicles having an axially shiftable ring gear |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
SE8306735A SE450944B (en) | 1983-12-06 | 1983-12-06 | RANGEVEXELLADA FOR MOTOR VEHICLES |
Publications (3)
Publication Number | Publication Date |
---|---|
SE8306735D0 SE8306735D0 (en) | 1983-12-06 |
SE8306735L SE8306735L (en) | 1985-06-07 |
SE450944B true SE450944B (en) | 1987-08-17 |
Family
ID=20353611
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
SE8306735A SE450944B (en) | 1983-12-06 | 1983-12-06 | RANGEVEXELLADA FOR MOTOR VEHICLES |
Country Status (7)
Country | Link |
---|---|
US (2) | US4667538A (en) |
JP (1) | JPH0788860B2 (en) |
DE (1) | DE3444562C2 (en) |
FR (1) | FR2556067B1 (en) |
GB (1) | GB2151316B (en) |
IT (1) | IT1178350B (en) |
SE (1) | SE450944B (en) |
Cited By (1)
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WO2002066850A1 (en) * | 2001-02-13 | 2002-08-29 | Volvo Lastvagnar Ab | Synchronization device of locking ring type |
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SE435831B (en) * | 1982-06-07 | 1984-10-22 | Volvo Ab | RANGEVEXELLADA FOR MOTOR VEHICLES |
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US4920828A (en) * | 1988-02-08 | 1990-05-01 | Mazda Motor Corporation | Planetary gear type transmission |
SE463477B (en) * | 1989-10-19 | 1990-11-26 | Saab Scania Ab | SYNCHRONIZING DEVICE ON A PLANET SWITCH |
IT1248575B (en) * | 1990-07-03 | 1995-01-19 | Zahnradfabrik Friedrichshafen | Sector-type gearbox for motor vehicle |
US5390347A (en) * | 1990-07-03 | 1995-02-14 | Zahnradfabrik Friedrichshafen Ag | Range change transmission for vehicles |
DE4222115C2 (en) * | 1991-12-16 | 2003-09-25 | Volkswagen Ag | Gear arrangement for vehicles |
DE4201849C2 (en) * | 1992-01-24 | 1996-10-17 | Index Werke Kg Hahn & Tessky | Spindle drive device for machine tools |
DE4439976A1 (en) * | 1994-11-09 | 1996-05-15 | Zahnradfabrik Friedrichshafen | Helical planetary gear |
SE504063C2 (en) * | 1994-12-23 | 1996-10-28 | Scania Cv Ab | Planetary gear and an auxiliary gearbox |
DE19733519A1 (en) * | 1997-08-02 | 1999-02-04 | Zahnradfabrik Friedrichshafen | Clutch |
DE19733518A1 (en) | 1997-08-02 | 1999-02-04 | Zahnradfabrik Friedrichshafen | Clutch |
DE19740305A1 (en) | 1997-09-13 | 1999-03-18 | Zahnradfabrik Friedrichshafen | Gear changing clutch |
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DE102008043676A1 (en) * | 2008-11-12 | 2010-05-20 | Zf Friedrichshafen Ag | Transmission device has planetary wheel set and hydraulically operated switching element, where planetary carrier of planetary wheel set stands in operative connection with transmission output shaft |
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-
1983
- 1983-12-06 SE SE8306735A patent/SE450944B/en not_active IP Right Cessation
-
1984
- 1984-11-28 US US06/676,411 patent/US4667538A/en not_active Ceased
- 1984-11-28 GB GB08429995A patent/GB2151316B/en not_active Expired
- 1984-12-05 IT IT49256/84A patent/IT1178350B/en active
- 1984-12-05 FR FR848418562A patent/FR2556067B1/en not_active Expired
- 1984-12-06 JP JP59258400A patent/JPH0788860B2/en not_active Expired - Fee Related
- 1984-12-06 DE DE3444562A patent/DE3444562C2/en not_active Revoked
-
1989
- 1989-11-24 US US07/445,051 patent/USRE33428E/en not_active Expired - Lifetime
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2002066850A1 (en) * | 2001-02-13 | 2002-08-29 | Volvo Lastvagnar Ab | Synchronization device of locking ring type |
US6824493B2 (en) | 2001-02-13 | 2004-11-30 | Volvo Lastvagnar Ab | Synchronization device of locking ring type |
Also Published As
Publication number | Publication date |
---|---|
DE3444562A1 (en) | 1985-06-20 |
FR2556067A1 (en) | 1985-06-07 |
GB2151316B (en) | 1987-05-28 |
IT8449256A0 (en) | 1984-12-05 |
SE8306735L (en) | 1985-06-07 |
IT8449256A1 (en) | 1986-06-05 |
GB2151316A (en) | 1985-07-17 |
SE8306735D0 (en) | 1983-12-06 |
GB8429995D0 (en) | 1985-01-09 |
JPH0788860B2 (en) | 1995-09-27 |
IT1178350B (en) | 1987-09-09 |
JPS60151461A (en) | 1985-08-09 |
USRE33428E (en) | 1990-11-06 |
DE3444562C2 (en) | 1997-12-11 |
US4667538A (en) | 1987-05-26 |
FR2556067B1 (en) | 1989-03-03 |
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